Rotating shaft mechanism, support device and folding apparatus

Abstract

The present application relates to the technical field of folding apparatuses. Provided are a rotating shaft mechanism, a support device and a folding apparatus, used for solving the issue of how to reduce the thickness of folding apparatuses. Specifically, a first swing arm of the rotating shaft mechanism is rotatably connected to a base, and a second swing arm thereof is rotatably connected to the base; N first drive gears are fixedly connected to the first swing arm, the N first drive gears being coaxially arranged; in the arrangement direction of the N first drive gears, gear teeth of the (i+1)-th first drive gear are offset with respect to gear teeth of the i-th first drive gear by a phase angle of βi; N second drive gears are fixedly connected to the second swing arm, the N second drive gears being coaxially arranged, and a second drive gear being meshed with a first drive gear; the second drive gears and the first drive gears are used for driving the first swing arm and the second swing arm to rotate in opposite directions, such that the rotating shaft mechanism moves between a deployed state and a folded state, wherein βi＞0°, 1≤i≤N-1, N≥2, and both N and i are integers.

Description

Rotating shaft mechanism, supporting device and folding device

[0001] The present application claims priority from the Chinese patent application No. 202411244158.3 filed on September 04, 2024, and entitled "Rotating shaft mechanism, supporting device and folding device", the content of which is incorporated herein by reference in its entirety. TECHNICAL FIELD

[0002] The present application relates to the technical field of folding device, and in particular to a rotating shaft mechanism, a supporting device and a folding device. BACKGROUND

[0003] With the progress of science and technology, large-screen devices are increasingly popular among consumers. In order to solve the problem of large size and inconvenience of carrying of traditional tablet devices, folding screen devices have emerged. The folding screen device includes a supporting device for supporting the folding screen, and the supporting device includes two side housings and a rotating shaft mechanism connected between the two side housings. A transmission mechanism is usually provided in the rotating shaft mechanism to ensure that the two side housings drive the two ends of the folding screen to rotate synchronously. However, with the increasing demand for thinness of the folding screen device, the rotating shaft mechanism also needs to be designed to be thinner. However, in the related art, in order to ensure the smoothness of transmission, the size of the components in the transmission mechanism is large, which makes the thickness of the rotating shaft mechanism large, limiting the thinness of the folding screen device. SUMMARY

[0004] Embodiments of the present application provide a rotating shaft mechanism, a supporting device and a folding device to solve the problem of how to reduce the thickness of the folding device.

[0005] To achieve the above-mentioned purpose, the embodiments of the present application adopt the following technical solutions:

[0006] In a first aspect, the embodiments of the present application provide a rotating shaft mechanism, which includes a base, a first swing arm, a second swing arm, N first drive gears and N second drive gears. The first swing arm is rotationally connected with the base. The second swing arm is rotationally connected with the base. The N first drive gears are fixedly connected with the first swing arm, and the N first drive gears are coaxially arranged. Along the arrangement direction of the N first drive gears, the teeth of the i+1th first drive gear are staggered by a phase angle β i with respect to the teeth of the ith first drive gear. The N second drive gears are fixedly connected with the second swing arm, and the N second drive gears are coaxially arranged. One second drive gear is engaged with one first drive gear; the second drive gear and the first drive gear are used to drive the first swing arm and the second swing arm to synchronously and reversely rotate relative to the base, so as to make the rotating shaft mechanism move between an unfolded state and a folded state. Wherein, β i > 0°, 1≤i≤N-1, N≥2, and N and i are integers.

[0007] The rotating shaft mechanism provided by the embodiments of the present application is characterized in that the phase angles of the teeth of every two adjacent first driving gears coaxially arranged are staggered, one second driving gear is engaged with one first driving gear among the N second driving gears coaxially arranged, so that when one of the first swing arm and the second swing arm rotates relative to the base, before the last tooth of the ith first driving gear and the last tooth of the ith second driving gear are engaged, one tooth of the (i+1)th first driving gear has been engaged with one tooth of the (i+1)th second driving gear. In this way, the total coincidence degree of the N first driving gears and the N second driving gears is greater than the coincidence degree of one first driving gear and one second driving gear, thereby increasing the stability of the transmission of the transmission mechanism including the N first driving gears and the N second driving gears. Compared with the transmission mechanism including only one first driving gear and one second driving gear, when the total coincidence degree of the transmission mechanism is the same, the coincidence degree of one first driving gear and one second driving gear among the N first driving gears and the N second driving gears can be smaller, which is beneficial to reducing the size of the first driving gear and the second driving gear, and further reducing the overall height and overall width of the rotating shaft mechanism, so as to be beneficial to reducing the thickness of the folding device as a whole.

[0008] In some possible implementation manners of the first aspect, the coincidence degree of one first driving gear and one second driving gear is ε1<1. The phase angle β i satisfies: β i ≤α1-kα

[0009] wherein, α z is the pitch angle of the first driving gear, and α1 is the angle rotated by the first driving gear from the engagement of one tooth to the disengagement of the tooth.

[0010] In this way, among the N first driving gears, there is always a first driving gear in the engaged state, so the total coincidence degree ε of the N first driving gears and the N second driving gears is greater than or equal to 1, so that the first swing arm and the second swing arm can rotate at the same angle in opposite directions relative to the base, and the rotating shaft mechanism has good synchronism and smoothness, and thus the folding device applying the rotating shaft mechanism has good synchronism and smoothness in opening and closing, and the user has a good experience.

[0011] In some possible implementation manners of the first aspect, the coincidence degree of one first driving gear and one second driving gear is k<ε1<k+1; the phase angle β i satisfies: β i ≤α1-kα z ;

[0012] wherein k≥1 and k is an integer; α z is the pitch angle of the first drive gear, and α1 is the angle of rotation of the first drive gear from the meshing-in of one tooth of the first drive gear to the meshing-out of the tooth.

[0013] In this way, the first drive gear set formed by the N first drive gears has a rotation angle region in which (k+1) teeth are continuously meshed as large as possible, which is conducive to making the total coincidence degree of the N first drive gears and the N second drive gears as large as possible, and further conducive to improving the synchronization and smoothness of the transmission of the transmission mechanism, thereby improving the user experience.

[0014] In some possible implementation manners of the first aspect, along the axial direction of the first drive gear: the teeth of the two adjacent first drive gears are spaced apart, and the teeth of the two adjacent second drive gears are spaced apart.

[0015] In this way, it can be prevented that, during the unfolding and folding of the rotating shaft mechanism, the projection of at least one of the N first drive gears on the N second drive gears is located on two second drive gears along the arrangement direction of the first axis and the second axis, and further it can be prevented that the transmission mechanism is stuck to cause the rotating shaft mechanism to be stuck.

[0016] In some possible implementation manners of the first aspect, the N first drive gears are one-piece structural members.

[0017] In some possible implementation manners of the first aspect, the N second drive gears are one-piece structural members.

[0018] In some possible implementation manners of the first aspect, the N first drive gears are one-piece structural members; and the N second drive gears are one-piece structural members.

[0019] In this way, the coaxialities of the N first drive gears are better, the phase angle tolerance between the first drive gears is easier to control, the coaxialities of the N second drive gears are better, the phase angle tolerance between the second drive gears is easier to control, and the tolerance accumulation can be prevented, thereby ensuring the total coincidence degree of the N first drive gears and the N second drive gears.

[0020] In some possible implementation manners of the first aspect, the peripheral surface of the first drive gear includes a first light surface and a first tooth surface, the first light surface is located on the side of the first tooth surface away from the second drive gear, and is connected with the surface of the first swing arm, and the first drive gear and the first swing arm are one-piece structural members.

[0021] In some possible implementation manners of the first aspect, the peripheral surface of the second drive gear includes a second light surface and a second tooth surface, the second light surface is located on the side of the first tooth surface away from the first drive gear, and is connected with the surface of the second swing arm, and the second drive gear and the second swing arm are one-piece structural members.

[0022] In some possible implementation ways of the first aspect, the peripheral surface of the first driving gear includes a first smooth surface and a first tooth surface, the first smooth surface is located on a side of the first tooth surface facing away from the second driving gear and is connected to a surface of the first swing arm, and the first driving gear and the first swing arm are an integral structure; the peripheral surface of the second driving gear includes a second smooth surface and a second tooth surface, the second smooth surface is located on a side of the first tooth surface facing away from the first driving gear and is connected to a surface of the second swing arm, and the second driving gear and the second swing arm are an integral structure.

[0023] In this way, the size of the first swing arm and the first driving gear in the first axis direction can be saved, and the size of the second swing arm and the second driving gear in the second axis direction can be saved, which is beneficial to making the overall structure of the rotating shaft mechanism more compact, and can reduce the difficulty of integrally forming the first swing arm and the first driving gear and the difficulty of integrally forming the second swing arm and the second driving gear.

[0024] In some possible implementation ways of the first aspect, the rotating shaft mechanism further includes a transmission component, and the transmission component is located between the first driving gears and the second driving gears; the transmission component is engaged with the N first driving gears and the N second driving gears.

[0025] In this way, the distance between the first axis and the second axis can be as large as possible, the radius of the water-drop-shaped screen space formed when the rotating shaft mechanism is in the folded state can be as large as possible, and the internal stress of the folding screen of the folding device using the rotating shaft mechanism can be prevented from being too large to reduce the service life of the folding screen.

[0026] In some possible implementation ways of the first aspect, the transmission component includes M groups of transmission gears, and the M groups of transmission gears are arranged along the arrangement direction of the N first driving gears and the N second driving gears; one group of transmission gears includes N transmission gears arranged along the axial direction of the first driving gear, and each two adjacent ones of the one first driving gear, the M transmission gears and the one second driving gear are engaged, and M is an even number greater than or equal to 2.

[0027] In this way, the transmission mechanism has good transmission stability and high transmission efficiency.

[0028] In some possible implementation manners of the first aspect, the transmission component includes N first racks and N second racks. The N first racks are arranged along an axial direction of the first driving gear, and each first rack extends in a first direction and is slidable relative to the base in the first direction, and one first rack is engaged with one first driving gear. The N second racks are arranged along a direction of the second axis, and the N second racks are parallel to and spaced apart from the N first racks, one second rack is fixedly connected with one first rack, and one second rack is engaged with one second driving gear. The first direction is perpendicular to a plane in which the central axis of the first driving gear and the central axis of the second driving gear are located.

[0029] In this way, the movement of one of the first swing arm and the second swing arm is transmitted to the other through the first rack and the second rack, so that the distance between the first axis and the second axis can be more flexible, and the design and assembly difficulty of the transmission component is lower.

[0030] In some possible implementation manners of the first aspect, the rotation shaft mechanism further includes a first damping cam, a second damping cam, and a first elastic member. The first damping cam is arranged on the base, and the first swing arm is configured to drive the first damping cam to rotate relative to the base when the first swing arm rotates relative to the base. The second damping cam is arranged on the base and is slidable relative to the base along an axial direction of the first driving gear, and the second damping cam is in contact with the first damping cam. The first elastic member is arranged on the base and configured to apply an elastic force to the second damping cam, the elastic force being directed to the first damping cam.

[0031] In this way, when the first swing arm rotates relative to the base, the first damping cam extrudes the second damping cam, so that the first elastic member is extruded to be elastically deformed, and then the first damping cam is provided with a reaction force, so that the folding device has a damping force in the process of folding or unfolding, facilitating the hovering of the folding device.

[0032] In some possible implementation manners of the first aspect, the rotation shaft mechanism further includes a third damping cam, a fourth damping cam, and a second elastic member. The third damping cam is arranged on the base, and the second swing arm is configured to drive the third damping cam to rotate relative to the base when the second swing arm rotates relative to the base. The fourth damping cam is arranged on the base and is slidable relative to the base along an axial direction of the second driving gear, and the fourth damping cam is in contact with the third damping cam. The second elastic member is arranged on the base and configured to apply an elastic force to the fourth damping cam, the elastic force being directed to the third damping cam.

[0033] In this way, when the second swing arm rotates relative to the base, the third damping cam extrudes the fourth damping cam, so that the second elastic member is extruded to generate elastic deformation, thereby providing a reaction force for the third damping cam, so that the folding device has a damping force in the folding or opening process, thereby doubling the damping force of the folding device in the folding and opening process, ensuring the reliability of the hovering of the folding device.

[0034] In some possible implementation manners of the first aspect, the second damping cam and the fourth damping cam are an integral structure.

[0035] In this way, by sleeving the second damping cam and the fourth damping cam on the first rotating shaft and the second rotating shaft respectively, the two can be limited relative to each other, without the need to additionally set a limiting structure to limit the rotation of the second damping cam and the fourth damping cam relative to the base, thereby simplifying the design and assembly difficulty of the rotating shaft mechanism.

[0036] In a second aspect, an embodiment of the present application provides a support device, which comprises a first shell, a second shell, and a rotating shaft mechanism. The rotating shaft mechanism is the rotating shaft mechanism in any of the implementation manners described above. The rotating shaft mechanism is located between the first shell and the second shell, the first swing arm is connected to the first shell, and the second swing arm is connected to the second shell.

[0037] Since the support device provided by the embodiment of the present application comprises the rotating shaft mechanism in the implementation manners described above, both can solve the same problem and achieve the same effect, which will not be described here again.

[0038] In a third aspect, an embodiment of the present application provides a folding device, which comprises a support device and a folding screen. The support device is the support device described above. The folding screen comprises a first part, a second part, and a third part connected in sequence, the first part is fixed to the first shell, the third part is fixed to the second shell, and the second part is supported on the rotating shaft mechanism.

[0039] Since the folding device provided by the embodiment of the present application comprises the support device in the implementation manners described above, both can solve the same problem and achieve the same effect, which will not be described here again.

[0040] In some possible implementation manners of the third aspect, the coincidence degree ε1 of the first driving gear and the second driving gear is less than 1. In the process that the folding device moves from the first state to the second state, when the first swing arm rotates a first rotation angle a relative to the base, the opening and closing torque of the folding device is a maximum torque Tmax; the first rotation angle a and the phase angle β satisfy: i satisfy:

[0041] The first state and the second state are one of an unfolded state and the other is a folded state; γ is an angle of rotation of the first driving gear when the folding device is in the first state and the first driving gear is just engaged with the tooth currently in the engaged state, and γ≥0°.

[0042] In this way, the number of the first driving gears in the engaged state in the first driving gear set is more at the position where the opening and closing torque of the folding device is maximum, and thus the load on each tooth is smaller, which is beneficial to prolong the service life of the rotating shaft structure and the folding device.

[0043] In some possible implementation manners of the third aspect, when the first swing arm rotates by a second rotation angle b relative to the base, the opening and closing torque of the folding device is T1, and 0.4≤T1 / Tmax≤0.6; when the first swing arm rotates from the second rotation angle b to a first rotation angle a relative to the base, the opening and closing torque of the folding device gradually increases, the second rotation angle b satisfies b≥α1-γ, and the first rotation angle a satisfies a≤α1-γ. i The following is satisfied:

[0044] In this way, the number of the first driving gears in the engaged state in the first driving gear set is more before the opening and closing torque of the folding device reaches the maximum, and thus the load on each tooth is smaller, which is beneficial to prolong the service life of the rotating shaft structure and the folding device.

[0045] In some possible implementation manners of the third aspect, the first rotation angle a further satisfies a<α1-γ.

[0046] In this way, all the first driving gears are in the engaged state at the position where the opening and closing torque of the folding device is maximum, which is beneficial to prolong the service life of the rotating shaft structure.

[0047] In some possible implementation manners of the third aspect, when the first swing arm rotates by a third rotation angle c relative to the base, the opening and closing torque of the folding device is T2, and 0.4≤T2 / Tmax≤0.6; when the first swing arm rotates from the first rotation angle a to the third rotation angle c relative to the base, the opening and closing torque of the folding device gradually decreases, and the third rotation angle c further satisfies c≤α1-γ.

[0048] In this way, all the first driving gears are in the engaged state at the position near the peak of the opening and closing torque of the folding device, and thus the load on each tooth is smaller, which is beneficial to prolong the service life of the rotating shaft structure and the folding device. BRIEF DESCRIPTION OF DRAWINGS

[0049] FIG. 1 is a perspective view of a folding device in an unfolded state according to some embodiments of the present application;

[0050] FIG. 2 is a partially exploded structural schematic view of the folding device shown in FIG. 1;

[0051] Fig. 3 is a schematic view of the folding device shown in Fig. 1 in a folded state;

[0052] Fig. 4 is another schematic view of the folding device shown in Fig. 1 in a partially exploded state;

[0053] Fig. 5 is a schematic view of the folding device shown in Fig. 4 in a folded state;

[0054] Fig. 6 is a schematic view of a hinge mechanism of the folding device shown in Fig. 3 in an unfolded state;

[0055] Fig. 7 is a schematic view of the hinge mechanism shown in Fig. 6 in a partially exploded state;

[0056] Fig. 8 is a schematic view of a portion of the hinge mechanism shown in Fig. 7;

[0057] Fig. 9 is a cross-sectional view of the hinge mechanism shown in Fig. 6 taken along line A-A;

[0058] Fig. 10 is a schematic view of a first door panel of the hinge mechanism shown in Fig. 6;

[0059] Fig. 11 is a schematic view of the hinge mechanism shown in Fig. 6 in a folded state;

[0060] Fig. 12 is a schematic view of a portion of the hinge mechanism shown in Fig. 8;

[0061] Fig. 13 is a cross-sectional view of the hinge mechanism shown in Fig. 11 taken along line B-B;

[0062] Fig. 14 is a schematic view of an end face coincidence of an external gear;

[0063] Fig. 15 is another schematic view of a portion of the hinge mechanism shown in Fig. 6;

[0064] Fig. 16 is a schematic view of a portion of the hinge mechanism shown in Fig. 15;

[0065] Fig. 17 is an axial view of a transmission mechanism of the hinge mechanism shown in Fig. 16;

[0066] Fig. 18 is a schematic view of an engagement region of a first drive gear;

[0067] Fig. 19 is a schematic view of engagement regions of a plurality of first drive gears;

[0068] Fig. 20 is a schematic view of engagement regions of a plurality of first drive gears;

[0069] Fig. 21 is a schematic view of engagement regions of a plurality of first drive gears;

[0070] Fig. 22 is another schematic view of a portion of the hinge mechanism shown in Fig. 3;

[0071] Fig. 23 is an exploded view of the hinge mechanism of Fig. 22;

[0072] Fig. 24 is a diagram of the opening and closing torsion curve of the folding device of Fig. 3;

[0073] Fig. 25 is a diagram of the meshing area of the first drive gears and the first swing arm relative to the rotation angle of the base;

[0074] Fig. 26 is a diagram of the hinge mechanism of Fig. 4 in an unfolded state;

[0075] Fig. 27 is an exploded view of the hinge mechanism of Fig. 26;

[0076] Fig. 28 is a diagram of a partial structure of the hinge mechanism of Fig. 27;

[0077] Fig. 29 is a diagram of the hinge mechanism of Fig. 26 in a folded state;

[0078] Fig. 30 is a sectional view of the hinge mechanism of Fig. 28;

[0079] Fig. 31 is a diagram of another partial structure of the hinge mechanism of Fig. 26;

[0080] Fig. 32 is a diagram of the hinge mechanism of Fig. 31 in a folded state;

[0081] Fig. 33 is a diagram of a partial structure of the hinge mechanism of Fig. 31;

[0082] Fig. 34 is a diagram of a partial structure of the hinge mechanism of Fig. 31.

[0083] 100 - folding device; 10 - folding screen; 11 - first part; 12 - second part; 121 - first transition section; 122 - second transition section; 123 - circular arc section; 13 - third part; 20 - supporting device; 21 - first housing; 22 - second housing; 23 - rotating shaft mechanism; 232 - base; 232a - first arc-shaped slot; 2321 - base body; 2322 - first cover plate; 2323 - limiting protrusion; 2324 - first fixing seat; 233 - first swing arm; 234 - second swing arm; 235 - third swing arm; 235a - first shaft hole; 2351 - first arc-shaped protrusion; 2352 - third arc-shaped protrusion; 236 - fourth swing arm; 237 - connecting piece; 2371 - first connecting piece; 2371a - second shaft hole; 2371b - first sliding slot; 2371c - second arc-shaped slot; 2371d - third arc-shaped slot; 2372 - second connecting piece; 238 - door plate; 2381 - first door plate; 2381a - first protruding part; 2381a1 - second arc-shaped protrusion; 2381b - second protruding part; 2381b1 - second sliding slot; 2382 - second door plate; 2383 - third door plate; 2384 - fourth door plate; 239 - transmission mechanism; 2391 - first driving gear; 2391a - first smooth surface; 2391b - first toothed surface; 2392 - second driving gear; 2392a - second smooth surface; 2392b - second toothed surface; 2393 - transmission component; 2393a - first meshing tooth; 2393b - second meshing tooth; 23931 - transmission gear; 23932 - first rack; 23932a - limiting hole; 23933 - second rack; 240 - first rotating shaft; 241 - second rotating shaft; 243 - fourth rotating shaft; 244 - damping structure; 2441 - first damping cam; 2442 - second damping cam; 2443 - third damping cam; 2444 - fourth damping cam; 2445 - first elastic member; 2446 - second elastic member; 2447 - third elastic member; 245 - fifth rotating shaft; 246 - sixth rotating shaft. DETAILED DESCRIPTION

[0084] In the embodiments of the present application, it should be noted that unless specifically defined and limited otherwise, the terms "mounting", "connecting" should be understood in a broad sense, for example, "connecting" can be detachable connection, or can be non-detachable connection; can be direct connection, or can be indirect connection through intermediate medium.

[0085] In the embodiments of the present application, it should be understood that the positional terms mentioned, such as "upper", "lower", "left", "right", "inner", "outer" and the like, are merely relative to the directions of the accompanying drawings, and therefore, the positional terms used are for better and clearer illustration and understanding of the embodiments of the present application, and do not indicate or imply that the devices or elements referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore cannot be understood as a limitation on the embodiments of the present application.

[0086] In the embodiments of the present application, the terms "first", "second", "third", "fourth", "fifth", "sixth" are only for descriptive purposes and cannot be understood as indicating or implying relative importance or implicitly indicating the number of the technical features indicated. Therefore, the features defined with "first", "second", "third", "fourth", "fifth", "sixth" can explicitly or implicitly include one or more of the features.

[0087] In the embodiments of the present application, the terms "include", "contain" or any other variants thereof are intended to cover non-exclusive inclusion, so that the processes, methods, articles or devices including a series of elements not only include those elements, but also include other elements not explicitly listed or inherent to such processes, methods, articles or devices. Without more limitations, the element defined by the statement "including a" does not exclude the presence of other identical elements in the process, method, article or device including the element.

[0088] In the embodiments of the present application, "and / or" is merely a description of the association relationship between the associated objects, which means that there can be three relationships, for example, A and / or B can represent the three cases of A alone, A and B together, and B alone. In addition, the character " / " herein generally represents an "or" relationship between the associated objects.

[0089] In the embodiments of the present application, it should be noted that the descriptions of "vertical", "parallel", "coaxial" respectively represent approximately vertical, approximately parallel and approximately coaxial within a certain error range, and the error range can be a range in which the deviation angle is less than or equal to 5°, 8° or 10° with respect to absolute vertical, absolute parallel and absolute coaxial, respectively, which is not limited here.

[0090] The application provides a folding device, which can be a kind of electronic device with a folding screen. The folding device includes but is not limited to a mobile phone, a tablet personal computer, a personal digital assistant (PDA), a handheld device with a wireless communication function, a computing device, a vehicle-mounted device, a wearable device, a virtual reality (VR) terminal device, an augmented reality (AR) terminal device, a wireless terminal in industrial control, a wireless terminal in self driving, a wireless terminal in remote medical, a wireless terminal in smart grid, a wireless terminal in transportation safety, a wireless terminal in smart city, a wireless terminal in smart home, and the like mobile terminal or fixed terminal. The shape of the folding device is not specifically limited in the embodiments of the application.

[0091] Please refer to FIG. 1 and FIG. 2, FIG. 1 is a perspective view of a folding device 100 in an unfolded state according to some embodiments of the application, and FIG. 2 is a partially exploded structural schematic view of the folding device 100 shown in FIG. 1. The folding device 100 is exemplarily illustrated as a handheld device with a wireless communication function, for example, a mobile phone, in the embodiments and the following embodiments. The folding device 100 is approximately rectangular and flat in the unfolded state. In order to facilitate the description of the following embodiments, an XYZ coordinate system is established for the folding device 100 in the unfolded state, and the length direction of the folding device 100 is defined as the X-axis direction, the width direction of the folding device 100 is defined as the Y-axis direction, and the thickness direction of the folding device 100 is defined as the Z-axis direction. It can be understood that the coordinate system of the folding device 100 can be flexibly set according to actual needs, which is not specifically limited herein. In some other embodiments, the shape of the folding device 100 can also be square, circular, elliptical, and the like.

[0092] The folding device 100 includes a folding screen 10 and a supporting device 20.

[0093] The folding screen 10 is used to display image, video and the like information. The folding screen 10 can be an organic light-emitting diode (OLED) screen, a micro organic light-emitting diode screen, a quantum dot light emitting diodes (QLED) screen, a liquid crystal display (LCD) and the like.

[0094] The folding screen 10 has a display area for displaying image information. The display area of the folding screen 10 is exposed so as to present image, video and the like information to the user. The folding screen 10 comprises a first part 11, a second part 12 and a third part 13 connected in sequence. In the embodiment shown in FIG. 1 and FIG. 2, the folding screen 10 is in an unfolded state, and the first part 11, the second part 12 and the third part 13 are arranged in sequence along the X-axis direction. In this way, the folding device 100 is folded in a horizontal direction, and the folding axis of the folding screen 10 is parallel to the Y-axis direction. In other embodiments, when the folding screen 10 is in the unfolded state, the first part 11, the second part 12 and the third part 13 can also be arranged in sequence along the Y-axis direction. In this way, the folding device 100 is folded in a vertical direction, i.e. the folding axis of the folding screen 10 is parallel to the X-axis direction. When the folding screen 10 is in the unfolded state, large-screen display can be realized to provide the user with more abundant information and better user experience.

[0095] At least the second part 12 of the folding screen 10 is a flexible screen structure. In this way, the second part 12 can be bent and deformed under external force, so as to fold the folding screen 10 from the unfolded state shown in FIG. 1 to the folded state. The first part 11 and the third part 13 of the folding screen 10 can also be flexible screen structures, or can be hard screen structures, or can be partially flexible screen structures and partially hard screen structures.

[0096] Please refer to FIG. 3, which is a structural schematic diagram of the folding device 100 shown in FIG. 1 in a folded state. The folding screen 10 in the folding device 100 is also in a folded state. Specifically, when the folding screen 10 is in the folded state, the first part 11 and the third part 13 of the folding screen 10 are approximately parallel and face each other. It should be noted that the included angle between the first part 11 and the third part 13 is within 30°, and both can be considered as approximately parallel. The first part 11 and the third part 13 face each other means that the display surface of the first part 11 faces the display surface of the third part 13.

[0097] When the folding screen 10 is in the folded state, the second part 12 is folded into a water drop shape, in which the second part 12 comprises a circular arc segment 123, a first transition segment 121 and a second transition segment 122. The first transition segment 121 is connected between the circular arc segment 123 and the first part 11. The second transition segment 122 is connected between the circular arc segment 123 and the third part 13. The distance between the end of the first part 11 connected with the first transition segment 121 and the end of the third part 13 connected with the second transition segment 122 is a third distance. The distance between the end of the circular arc segment 123 connected with the first transition segment 121 and the end of the circular arc segment 123 connected with the second transition segment 122 is a fourth distance, which is greater than the third distance. It can be understood that, when the folding device 100 is in the folded state, the second part 12 of the folding screen 10 can also be folded into other shapes according to actual needs, which is not limited in the present application.

[0098] Please refer to FIG. 2 and FIG. 3 together, the support device 20 is used to carry the folding screen 10. When the folding device 100 is in the folded state, the support device 20 is protected outside the folding screen 10, and the folding screen 10 is invisible to the user, i.e. the folding device 100 is an inner folding device, which can prevent the folding screen 10 from being scratched by a hard object.

[0099] In other embodiments, please refer to FIG. 4 and FIG. 5 together, FIG. 4 is another partial structural schematic diagram of the folding device 100 shown in FIG. 1, and FIG. 5 is a structural schematic diagram of the folding device 100 shown in FIG. 4 in the folded state. The difference between the embodiments shown in FIG. 4 and FIG. 5 and the embodiments shown in FIG. 2 and FIG. 3 is that, when the folding device 100 is in the folded state, the folding screen 10 is located outside the support device 20, and the folding screen 10 is visible to the user, i.e. the folding device 100 is an outer folding device, which can realize the display of video and image in the folded state. At this time, the first part 11 and the third part 13 of the folding screen 10 are approximately parallel and opposite. The first part 11 and the third part 13 opposite means that the display surfaces of the first part 11 and the third part 13 are opposite. The second part 10 is folded into a U shape, in which the aforementioned third distance is equal to the aforementioned fourth distance.

[0100] Please refer to FIG. 3-FIG. 5 together, the support device 20 comprises a first housing 21, a second housing 22 and a hinge mechanism 23. The first housing 21 carries the first part 11, and the second housing 22 carries the third part 13. The hinge mechanism 23 is connected between the first housing 21 and the second housing 22 and carries the second part 12, i.e. the second part 12 of the folding screen 10 is supported on the hinge mechanism 23. The hinge mechanism 23 is used to realize the rotation between the second housing 22 and the first housing 21 to support the folding of the folding screen 10 between the unfolded state and the folded state.

[0101] The first shell 21 can include a middle frame and a back cover connected together. The first part 11 of the folding screen 10 can be fixed to the middle frame of the first shell 21, i.e., the first part 11 is fixed to the first shell 21, specifically, the first part 11 can be adhesively fixed to the first shell 21. The back cover is located on the side of the middle frame away from the first part 11, and the back cover can be replaced by a display screen (such as an LCD display screen). A receiving cavity is formed between the middle frame and the back cover, which is used to accommodate electronic components such as a main board, a camera module, a battery, etc. On this basis, the first shell 21 can be connected to the rotation shaft mechanism 23 by means of the middle frame, or can be connected to the rotation shaft mechanism 23 by means of the back cover. The following embodiments are described by taking the first shell 21 connected to the rotation shaft mechanism 23 by means of the middle frame as an example.

[0102] Similarly, the second shell 22 can also include a middle frame and a back cover connected together. The third part 13 of the folding screen 10 can be fixed to the middle frame of the second shell 22, i.e., the third part 13 is fixed to the second shell 22, specifically, the third part 13 can be adhesively fixed to the second shell 22. The back cover is located on the side of the middle frame away from the third part 13, and the back cover can also be replaced by a display screen (such as an LCD display screen). A receiving cavity is formed between the middle frame and the back cover, which is used to accommodate electronic components such as a sub-board, a speaker module, an array, a battery, etc. On this basis, the second shell 22 can be connected to the rotation shaft mechanism 23 by means of the middle frame, or can be connected to the rotation shaft mechanism 23 by means of the back cover. The following embodiments are described by taking the second shell 22 connected to the rotation shaft mechanism 23 by means of the middle frame as an example.

[0103] In other embodiments, the support device 20 can further include a third shell (not shown in the figure), which is rotatably connected to the side of the first shell 21 or the second shell 22 away from the rotation shaft mechanism 23. At the same time, the folding screen 10 can further include a fourth part (not shown in the figure), which is connected to the first part or the third part. The fourth part is supported on the third shell, i.e., the fourth part is fixed to the third shell. In this way, the folding screen device 100 can be folded multiple times, which is conducive to further reducing the volume of the folding screen device 100 in the folded state. In other embodiments, the folding screen 10 can only include the first part 11 or the third part 13. In other embodiments, the folding device 100 can not include the folding screen 10, i.e., the support device 20 and the components arranged on the support device 20 form the folding device 100.

[0104] Please refer to FIG. 6-FIG. 8, FIG. 6 is a structural schematic diagram of the hinge mechanism 23 of the folding device 100 shown in FIG. 3 in an unfolded state, FIG. 7 is an exploded structural schematic diagram of the hinge mechanism 23 shown in FIG. 6, and FIG. 8 is a partial structural schematic diagram of the hinge mechanism 23 shown in FIG. 7. FIG. 8 is a partial structural schematic diagram of the hinge mechanism 23 shown in FIG. 6 after hiding the two door plates 238 and the first cover plate 2322. The hinge mechanism 23 includes a base 232, a first swing arm 233, a second swing arm 234, a third swing arm 235, a fourth swing arm 236, a connecting piece 237, door plates 238, and a transmission mechanism 239.

[0105] The base 232 provides a position reference datum, and the material of the base 232 includes but is not limited to metal and plastic. The base 232 is a split structure, and the base 232 includes a base body 2321, a first cover plate 2322, and a first fixed seat 2324 between the base body 2321 and the first cover plate 2322. The first cover plate 2322 is arranged on the front side of the base body 2321 and connected with the base body 2321 and the first fixed seat 2324. Specifically, the first cover plate 2322 can be connected with the base body 2321 and the first fixed seat 2324 by screws. It should be noted that the front side of the base body 2321 refers to the side of the base body 2321 facing the folding screen. In the following embodiments, the "rear side" of other components in the hinge mechanism 23 refers to the side of the described component away from the folding screen, and the "front side" refers to the side of the described component facing the folding screen, which will not be described in the following embodiments.

[0106] Please continue to refer to FIG. 6-FIG. 8, the connecting piece 237 includes a first connecting piece 2371 and a second connecting piece 2372, and the door plates 238 include a first door plate 2381 and a second door plate 2382. The third swing arm 235 and the fourth swing arm 236 can be referred to as main swing arms, and the third swing arm 235 and the fourth swing arm 236 can be arranged at opposite ends of the base 232 along the X-axis direction. The first swing arm 233 and the second swing arm 234 can be referred to as auxiliary swing arms, and the first swing arm 233 and the second swing arm 234 can be arranged at opposite ends of the base 232 along the X-axis direction. Specifically, the first swing arm 233 and the third swing arm 235 are located on the same side of the base 232, and the second swing arm 234 and the fourth swing arm 236 are located on the same side of the base 232. One end of the third swing arm 235 can be rotatably connected with the base 232, and the other end can be rotatably connected with the first connecting piece 2371. The extension direction of the rotation axis between the third swing arm 235 and the base 232 and the extension direction of the rotation axis between the third swing arm 235 and the first connecting piece 2371 are parallel to the Y-axis direction.

[0107] Specifically, please refer to FIG. 8 and FIG. 9, FIG. 9 is a sectional view of the rotating shaft mechanism 23 shown in FIG. 6 at the line A-A. The end of the third swing arm 235 close to the base 232 has a first arc-shaped protrusion 2351, the base body 2321 and the first cover plate 2322 enclose a first arc-shaped slot 232a which is adapted to the first arc-shaped protrusion 2351, the first arc-shaped protrusion 2351 is slidably arranged in the first arc-shaped slot 232a to realize the rotatable connection between the third swing arm 235 and the base 232, the center line of the first arc-shaped slot 232a is the rotation axis of the third swing arm 235 and the base 232. In other embodiments, the third swing arm 235 and the base 232 can also be rotatably connected through a rotating shaft hinge.

[0108] The end of the third swing arm 235 away from the base 232 has a third arc-shaped protrusion 2352, the first connecting member 2371 has a third arc-shaped slot 2371d, the third arc-shaped protrusion 2352 is slidably arranged in the third arc-shaped slot 2371d to realize the rotatable connection between the third swing arm 235 and the first connecting member 2371, the center line of the third arc-shaped slot 2371d is the rotation axis of the third swing arm 235 and the first connecting member 2371. In other embodiments, the third swing arm 235 and the first connecting member 2371 can also be rotatably connected through a rotating shaft hinge. On this basis, the surface of the first connecting member 2371 facing the base 232 has a first sliding groove 2371b, the first sliding groove 2371b extends in a direction perpendicular to the first axis, and the end of the first swing arm 233 away from the base 232 is slidably arranged in the first sliding groove 2371b. In other embodiments, the first connecting member 2371 can also be rotatably connected with the first swing arm 233 and slidably connected with the third swing arm 235.

[0109] The end of the first swing arm 233 is rotatably connected with the base 232 around the first axis, the extension direction of the first axis is parallel to the Y-axis direction. In the embodiment shown in FIG. 7 and FIG. 8, the rotating shaft mechanism 23 further includes a first rotating shaft 240, the first rotating shaft 240 is arranged in the first fixed seat 2324 of the base 232 and gap-fitted with the base body 2321 at both ends, the end of the first swing arm 233 close to the base 232 is sleeved on the first rotating shaft 240, and the axis of the first rotating shaft 240 forms the first axis. In some examples, the first rotating shaft 240 can be fixedly connected with the base 232, and the first swing arm 233 can be rotatably connected with the first rotating shaft 240. In other examples, the first rotating shaft 240 can be rotatably connected with the base 232, and the first swing arm 233 can be fixedly connected with the first rotating shaft 240.

[0110] Similarly, one end of the second swing arm 234 is rotatably connected with the base 232 around a second axis, the extension direction of the second axis is parallel to the Y-axis direction, that is, the second axis is parallel to the first axis. In the embodiment shown in FIGS. 7 and 8, the rotating shaft mechanism 23 further comprises a second rotating shaft 241, which is arranged in the first fixed seat 2324 of the base 232 and is in clearance fit with the base body 2321 at both ends, and the end of the second swing arm 234 close to the base 232 is sleeved on the second rotating shaft 241, and the axis of the second rotating shaft 241 forms the second axis. The connection relationship between the second rotating shaft 241 and the second swing arm 234, the base 232 can refer to the connection relationship between the first rotating shaft 240 and the first swing arm 233, the base 232, which will not be repeated here.

[0111] On the basis of the above, please refer to FIGS. 6, 8-10, and FIG. 10 is a structural schematic view of the first door plate 2381 of the rotating shaft mechanism 23 shown in FIG. 6. The first door plate 2381 is located on the front side of the first connecting piece 2371, and the end surface of the first connecting piece 2371 arranged along the Y-axis direction has a second arc-shaped groove 2371c, and the back surface of the first door plate 2381 has a first protruding part 2381a, one of the first protruding parts 2381a has a second arc-shaped protruding block 2381a1, and one of the second arc-shaped protruding blocks 2381a1 is slidably arranged in one of the second arc-shaped grooves 2381a1 to realize the rotatable connection between the first door plate 2381 and the first connecting piece 2371. Based on this, the rotating shaft mechanism 23 further comprises a fourth rotating shaft 243, which is arranged in the third swing arm 235 and has an axis parallel to the first axis. The back surface of the first door plate 2381 further has a second protruding part 2381b, which has a second sliding groove 2381b1, and the fourth rotating shaft 243 is slidably arranged in the second sliding groove 2381b1. In some other embodiments, the first connecting piece 2371 has a second arc-shaped protruding block, the first protruding part 2381a has a second arc-shaped groove, and the second arc-shaped protruding block is slidably arranged in one of the second arc-shaped grooves.

[0112] Correspondingly, the rotatable connection between the fourth swing arm 236 and the base 232 can refer to the rotatable connection between the third swing arm 235 and the base 232; the rotatable connection between the fourth swing arm 236 and the second connecting piece 2372 can refer to the rotatable connection between the third swing arm 235 and the first connecting piece 2371; the sliding connection between the second swing arm 234 and the second connecting piece 2372 can refer to the sliding connection between the first swing arm 233 and the first connecting piece 2371; and the connection between the second door plate 2382 and the second connecting piece 2372, the fourth swing arm 236 can refer to the connection between the first door plate 2381, the first connecting piece 2371, and the third swing arm 235, which will not be repeated here.

[0113] On this basis, the first connecting member 2371 is fixedly connected with the first shell 21, that is, the first swing arm 233 is connected with the first shell 21 through the first connecting member 2371. The second connecting member 2372 is fixedly connected with the second shell 22, that is, the second swing arm 234 is connected with the second shell 22 through the second connecting member 2372.

[0114] Please refer to FIG. 6 and FIG. 11, which is a structural schematic diagram of the hinge mechanism 23 in the folding state. When the first shell 21 and the second shell 22 drive the first connecting member 2371 and the second connecting member 2372 to rotate towards each other, the first connecting member 2371 drives the third swing arm 235 to rotate synchronously, and the first connecting member 2371 and the third swing arm 235 can extend relative to the first swing arm 233, the second connecting member 2372 drives the fourth swing arm 236 to rotate synchronously, and the second connecting member 2372 and the fourth swing arm 236 can extend relative to the second swing arm 234, so as to increase the length of the hinge mechanism 23 in the plane perpendicular to the first axis. At the same time, the third swing arm 235 connected with the first door plate 2381 drives the first door plate 2381 to rotate relative to the first connecting member 2371, and the direction of the rotation of the first door plate 2381 relative to the first connecting member 2371 is the same as the direction of the rotation of the first connecting member 2371 relative to the base 232. The fourth swing arm 236 connected with the second door plate 2382 drives the second door plate 2382 to rotate relative to the second connecting member 2372, and the direction of the rotation of the second door plate 2382 relative to the second connecting member 2372 is the same as the direction of the rotation of the second connecting member 2372 relative to the base 232, so as to make the first door plate 2381, the second door plate 2382 and the base 232 enclose a screen containing space containing the second part of the folding screen 10.

[0115] Please continue to refer to FIG. 6 and FIG. 11, when the first shell 21 and the second shell 22 drive the first connecting piece 2371 and the second connecting piece 2372 to rotate away from each other, the first connecting piece 2371 drives the third swing arm 235 to rotate synchronously, and the first connecting piece 2371 and the third swing arm 235 can retract relative to the first swing arm 233, the second connecting piece 2372 drives the fourth swing arm 236 to rotate synchronously, and the second connecting piece 2372 and the fourth swing arm 236 can retract relative to the second swing arm 234, so as to reduce the length of the rotating shaft mechanism 23 in the plane perpendicular to the first axis. At the same time, the third swing arm 235 connected with the first door plate 2381 drives the first door plate 2381 to rotate relative to the first connecting piece 2371, and the direction of rotation of the first door plate 2381 relative to the first connecting piece 2371 is the same as the direction of rotation of the first connecting piece 2371 relative to the base 232, and the fourth swing arm 236 connected with the second door plate 2382 drives the second door plate 2382 to rotate relative to the second connecting piece 2372, and the direction of rotation of the second door plate 2382 relative to the second connecting piece 2372 is the same as the direction of rotation of the second connecting piece 2372 relative to the base 232, so as to form a support surface with the first door plate 2381 and the second door plate 2382.

[0116] On the basis of the above, please refer to FIG. 8 and FIG. 12, FIG. 12 is a partial structure diagram of the rotating shaft mechanism 23 shown in FIG. 8. The rotating shaft mechanism 23 further comprises a damping structure 244, the damping structure 244 comprises a first damping cam 2441, a second damping cam 2442, a third damping cam 2443, a fourth damping cam 2444, a first elastic piece 2445, a second elastic piece 2446 and a third elastic piece 2447.

[0117] The first damping cam 2441 is arranged on the base 232, and the first swing arm 233 can drive the first damping cam 2441 to rotate relative to the base 232 when the first swing arm 233 rotates relative to the base 232. Specifically, the first damping cam 2441 is arranged on the first swing arm 233 and is sleeved on the first rotating shaft 240. In the embodiment shown in FIG. 8 and FIG. 12, the first damping cam 2441 is arranged on one surface of the first swing arm 233 arranged along the first axis direction. The first damping cam 2441 can be an integral molding structure with the first swing arm 233, or can be arranged on the first swing arm 233 by clamping, threaded connection or the like, that is, the first damping cam 2441 is arranged on the base 232 through the first swing arm 233 and the first rotating shaft 240, and the first damping cam 2441 can rotate relative to the base 232 when the first swing arm 233 rotates relative to the base 232.

[0118] The second damping cam 2442 is sleeved on the first rotating shaft 240 and can slide relative to the first rotating shaft 240, that is, the second damping cam 2442 is arranged on the base 232 through the first rotating shaft 240 and can slide along the direction of the first axis relative to the base 232. The surface of the first damping cam 2441 facing the second damping cam 2442 has at least two protruding portions arranged at intervals in the circumferential direction of the first rotating shaft 240, and the surface of the second damping cam 2442 facing the first damping cam 2441 has at least two protruding portions arranged at intervals in the circumferential direction of the first rotating shaft 240, and the second damping cam 2442 is in contact with the first damping cam 2441.

[0119] The first elastic member 2445 can include a first damping spring, the first damping spring is sleeved on the first rotating shaft 240, and the two ends of the first damping spring are in contact with or connected to the second damping cam 2442 and the base body 2321 respectively, that is, the first elastic member 2445 is arranged on the base 232 through the first rotating shaft 240, and is used for applying an elastic force to the second damping cam 2442 and pointing to the first damping cam 2441. In other embodiments, the first elastic member 2445 can also be an elastic member such as elastic rubber which has the ability of elastic deformation.

[0120] In this way, when the first swing arm 233 rotates relative to the base 232, the first damping cam 2441 extrudes the second damping cam 2442, so that the first damping spring is extruded to produce elastic deformation, thereby providing a reaction force for the first damping cam 2441, so that the folding equipment 100 has a damping force in the process of folding or opening, facilitating the hovering of the folding equipment 100.

[0121] On the basis of the above, the third damping cam 2443 is arranged on the base 232, and the second swing arm 234 can drive the third damping cam 2443 to rotate relative to the base 232 when the second swing arm 234 rotates relative to the base 232. The fourth damping cam 2444 is arranged on the base 232 and can slide along the direction of the second axis relative to the base 232, and the fourth damping cam 2444 is in contact with the third damping cam 2443. On this basis, the second elastic member 2446 is arranged on the base 232 and is used for applying an elastic force to the fourth damping cam 2444 and pointing to the third damping cam 2443. Specifically, the connection structure between the third damping cam 2443, the second swing arm 234, the second rotating shaft 241, the fourth damping cam 2444, the second elastic member 2446 can refer to the connection structure between the first damping cam 2441, the first swing arm 233, the first rotating shaft 240, the second damping cam 2442, the first elastic member 2445, which will not be described here.

[0122] In this way, when the second swing arm 234 rotates relative to the base 232, the third damping cam 2443 extrudes the fourth damping cam 2444, so that the second elastic member 2446 is extruded to produce elastic deformation, thereby providing a reaction force for the third damping cam 2443, so that the folding device 100 has a damping force in the folding or opening process, thereby making the folding device 100 have double damping force in the folding and opening process, and ensuring the reliability of the hovering of the folding device 100.

[0123] On this basis, the second damping cam 2442 and the fourth damping cam 2444 are an integral structure. In this way, the second damping cam 2442 and the fourth damping cam 2444 are respectively sleeved on the first rotating shaft 240 and the second rotating shaft 241, and can be limited relative to each other, without the need to additionally set a limiting structure to limit the rotation of the second damping cam 2442 and the fourth damping cam 2444 relative to the base 232, thereby simplifying the design and assembly difficulty of the rotating shaft mechanism 23, and improving the structural compactness of the rotating shaft mechanism 23.

[0124] Based on this, the third elastic member 2447 can be located between the first elastic member 2445 and the second elastic member 2446, and the two ends of the third elastic member 2447 are respectively in contact with or connected to the second damping cam 2442 and the base body 2321. Specifically, the third elastic member 2447 can be sleeved on the positioning shaft fixedly connected with the second damping cam 2442, and the two ends of the third elastic member 2447 can also be fixedly connected to the second damping cam 2442 and the base body 2321 respectively. In this way, when the first swing arm 233 and the second swing arm 234 rotate relative to the base 232, the third elastic member 2447 is extruded to produce elastic deformation, thereby providing a reaction force for the first damping cam 2441 and the third damping cam 2443, further increasing the damping force of the folding device 100 in the folding or unfolding process, and ensuring the reliability of the hovering of the folding device 100. In some other embodiments, the damping structure 244 can also not include the third elastic member 2447. In some other embodiments, the damping structure 244 can also not include the third damping cam 2443, the fourth damping cam 2444 and the second elastic member 2446.

[0125] Please refer to FIG. 8, FIG. 12 and FIG. 13, and FIG. 13 is a sectional view of the rotating shaft mechanism 23 at the line B-B shown in FIG. 11. The transmission mechanism 239 comprises a first driving gear 2391, a second driving gear 2392 and a transmission component 2393. In the embodiment shown in FIG. 12 and FIG. 13, the transmission component 2393 comprises M transmission gears 23931, M≥2 and M is even. The first driving gear 2391 is fixedly connected with the first swing arm 233, and the central axis of the first driving gear 2391 is collinear with the first axis. The second driving gear 2392 is fixedly connected with the second swing arm 234, and the central axis of the second driving gear 2392 is collinear with the second axis. Specifically, the first driving gear 2391 can be sleeved on the first rotating shaft 240 and fixed to the first rotating shaft 240 by key connection, or the first driving gear 2391 can be formed as an integral gear shaft with the first rotating shaft 240. The second driving gear 2392 can be sleeved on the second rotating shaft 241 and fixed to the second rotating shaft 241 by key connection, or the second driving gear 2392 can be formed as an integral gear shaft with the second rotating shaft 241.

[0126] The peripheral surface of the first driving gear 2391 comprises a first smooth surface 2391a and a first tooth surface 2391b connected with each other, and the first smooth surface 2391a is located on the side of the first tooth surface 2391b away from the second driving gear 2392, i.e. the first driving gear 2391 is an incomplete gear, and the actual number of teeth of the first driving gear 2391 is less than the theoretical number of teeth. The first smooth surface 2391a is an arc surface, and the center line of the first smooth surface 2391a is collinear with the central axis of the first driving gear 2391. The curvature radius of the first smooth surface 2391a can be equal to the addendum circle radius of the first driving gear 2391, so as to increase the strength of the first driving gear 2391. In other embodiments, the curvature radius of the first smooth surface 2391a can be less than the addendum circle radius of the first driving gear 2391, so as to reduce the overall size of the first driving gear 2391.

[0127] Similarly, the peripheral surface of the second driving gear 2392 comprises a second smooth surface 2392a and a second tooth surface 2392b connected with each other, and the second smooth surface 2392a is located on the side of the second tooth surface 2392b away from the first driving gear 2391, i.e. the second driving gear 2392 is an incomplete gear, and the actual number of teeth of the second driving gear 2392 is less than the theoretical number of teeth. Similarly, the second smooth surface 2392a can be an arc surface, and the curvature radius of the second smooth surface 2392a can be equal to or less than the addendum circle radius of the second driving gear 2392.

[0128] M transmission gears 23931 are located between the first drive gear 2391 and the second drive gear 2392, i.e., the transmission component 239 is located between the first drive gear 2391 and the second drive gear 2392. The M transmission gears 23931 are arranged along the arrangement direction of the first axis and the second axis, specifically, the M transmission gears 23931 can be arranged along a straight line or along a curve. Each adjacent two of the first drive gear 2391, the M transmission gears 23931 and the second drive gear 2392 are in meshing, i.e., the first drive gear 2391 and the second drive gear 2392 are indirectly in meshing through the transmission component 2393. In this way, the transmission mechanism 239 can drive the first swing arm 233 and the second swing arm 234 to synchronously and reversely rotate relative to the base 232, and then transmit the movement and load of one of the first shell 21 and the second shell 22 to the other, so that the first shell 21 and the second shell 22 can move synchronously. That is, the first drive gear 2391 and the second drive gear 2392 are used to drive the first swing arm 233 and the second swing arm 234 to synchronously and reversely rotate relative to the base 232, so as to drive the rotation shaft mechanism 23 to move between the unfolded state shown in FIG. 6 and the folded state shown in FIG. 11, thereby ensuring the symmetry and synchronism of the folding device 100 in the folding and unfolding process, and improving the user experience.

[0129] When the folding device 100 is in the unfolded state, the overall height of the rotation shaft mechanism 23 is a key factor affecting the thickness (thickness in the Z-axis direction) of the folding device 100, and the overall height of the transmission mechanism 239 is a key factor affecting the height of the rotation shaft mechanism 23, i.e., the diameters of the gears in the transmission mechanism 239 are key factors affecting the overall height of the rotation shaft mechanism 23. When the folding device 100 is in the folded state, the overall width (width in the X-axis direction) of the rotation shaft mechanism 23 is a key factor affecting the thickness (thickness in the X-axis direction) of the folding device 100, and the overall width of the transmission mechanism 239 is a key factor affecting the width of the rotation shaft mechanism 23, i.e., the diameters of the gears in the transmission mechanism 239 are also key factors affecting the overall width of the rotation shaft mechanism 23. Therefore, the smaller the diameters of the gears in the transmission mechanism 239, the more conducive to the thinning of the folding device 100.

[0130] However, the reduction of the size of the gears in the transmission mechanism will affect the coincidence degree of the meshing gears in the transmission mechanism, and then affect the smoothness of the transmission. Specifically, please refer to FIG. 14, which is an end face coincidence degree definition diagram of externally meshing gears. The end face coincidence degree ε of the externally meshing gears can be calculated by the following relationship formula I:

[0131] Wherein, z1 is the number of teeth of the gear with the center O1 of the reference circle, z2 is the number of teeth of the gear with the center O2 of the reference circle; α a1The addendum pressure angle of the gear with the center of the pitch circle O1, α a2 The addendum pressure angle of the gear with the center of the pitch circle O1; α' is the meshing angle of the two gears in meshing, that is, the circumferential velocity direction of the node P of the two gears in meshing transmission and the acute angle between the meshing line N1N2.

[0132] As can be seen from the relationship one, the coincidence degree ε of the two gears in meshing is irrelevant to the modulus, and the main parameters affecting the coincidence degree ε are the number of teeth z and the meshing angle α', the greater the number of teeth of the gear, the greater the coincidence degree ε of the two gears in meshing, and the better the transmission continuity and stability of the transmission mechanism 239. However, in the case that the modulus of each gear in the transmission mechanism 239 is unchanged, the greater the number of teeth of the gear, the greater the size of the gear. With the demand for thinness of the folding device 100, the size of the gear of the transmission mechanism 239 allowed is getting smaller and smaller, and the coincidence degree ε of the two gears in meshing of the transmission mechanism 239 is also getting smaller and smaller, and the transmission stability of the transmission mechanism 239 is also getting worse and worse. When the size of the gear is reduced to a certain extent, the coincidence degree ε of the gears in meshing of the transmission mechanism 239 may even be less than 1, that is, along the rotation direction of the gear, when the previous tooth of one gear is out of meshing, the next tooth has not yet entered the meshing state, thereby causing the transmission to be discontinuous and interrupted, and further causing the opening and closing process of the folding device 100 to be jerky, in addition, it also causes the deformation amount of the first elastic member 2445 and the second elastic member 2446 to be inconsistent, and further causes the integrated structure formed by the second damping cam 2442 and the fourth damping cam 2444 to be jammed with the first rotating shaft 240 and the second rotating shaft 241, which seriously affects the user experience.

[0133] In order to solve the above problems, please refer to FIGS. 15-17, FIG. 15 is another partial structure schematic diagram of the rotating shaft mechanism 23 shown in FIG. 6, FIG. 16 is a partial structure schematic diagram of the rotating shaft mechanism 23 shown in FIG. 15, and FIG. 17 is an axial view of the transmission mechanism 239 of the rotating shaft mechanism 23 shown in FIG. 16, wherein (a) of FIG. 17 is an axial view of the transmission mechanism 239 when the rotating shaft mechanism 23 is in the unfolded state, and (b) of FIG. 17 is an axial view of the transmission mechanism 239 when the rotating shaft mechanism 23 is in the folded state. The embodiment shown in FIGS. 15-17 is different from the embodiment shown in FIGS. 8 and 12 in that the transmission mechanism 239 comprises N first driving gears 2391, the N first driving gears 2391 are fixedly connected with the first swing arm 233, and are arranged along the direction of the first axis, that is, the N first driving gears 2391 are coaxially arranged. Along the arrangement direction of the N first driving gears 2391, the teeth of the i+1th first driving gear 2391 are staggered by a phase angle β i with respect to the teeth of the ith first driving gear 2391 in the opposite direction of the rotation direction of the first driving gear 2391. i> 0°, 1≤i≤N-1, N≥2, and N and i are integers.

[0134] It should be noted that the phase angle β i It should also be satisfied that β i < α z That is, the phase angle β i is greater than 0° and less than α z , where α z is the pitch angle of the first drive gear 2391, which can be calculated from the following relationship three.

[0135] Similarly, the transmission mechanism 239 includes N second drive gears 2392, which are fixedly connected with the second swing arm 234 and arranged along the direction of the second axis, that is, the N second drive gears 2392 are coaxially arranged. Along the arrangement direction of the N second drive gears 2392, the teeth of the i+1th second drive gear 2392 are staggered with the teeth of the ith second drive gear 2392 by a phase angle β i , where β i > 0°, 1≤i≤N-1, N≥2, and N and i are integers. Based on this, the first drive gear 2391 and the second drive gear 2392 correspond one by one, and one first drive gear 2391 and one second drive gear 2392 are engaged. The values of the phase angle β i corresponding to different values of i can be the same, that is, along the arrangement direction of the N first drive gears 2391, the teeth of every adjacent two first drive gears 2391 are staggered by the same phase angle. In other embodiments, the values of the phase angle β i corresponding to different values of i can also be different.

[0136] In the embodiments shown in FIGS. 15-17, the number of first drive gears 2391 and the number of second drive gears are both 2, and the phase angle is 22.5°. In other embodiments, the number of first drive gears 2391 and the number of second drive gears 2392 can also be 3, 4, 5, 6, 7, etc., which can be selected according to the load required to be transmitted between the first shell 21 and the second shell 22.

[0137] In this way, when one of the first swing arm 233 and the second swing arm 234 rotates relative to the base 232 under the action of the corresponding housing, in the two adjacent teeth of the ith first drive gear 2391, before the latter tooth of the ith first drive gear 2391 and the latter tooth of the ith second drive gear 2392 enter into engagement, one tooth of the ith+1 first drive gear 2391 has already engaged with one tooth of the ith+1 second drive gear 2392, so that the total coincidence degree of the N first drive gears 2391 and the N second drive gears 2392 is greater than the coincidence degree of one first drive gear 2391 and one second drive gear 2392, thereby increasing the stability of the transmission of the transmission mechanism 239. In the case of the same total coincidence degree of the transmission mechanism 239, it is beneficial to reduce the size of the first drive gear 2391 and the second drive gear 2392, and thereby reduce the overall height and overall width of the rotating shaft mechanism 23, so as to facilitate the reduction of the thickness of the folding device 100.

[0138] On the basis of the above, please refer to FIGS. 15-17, the N first drive gears 2391 and the N second drive gears 2392 can be indirectly engaged through a transmission component 2393. That is, the transmission component 2393 is engaged with the N first drive gears 2391 and the N second drive gears 2392. Specifically, the transmission component 2393 includes M sets of transmission gears 23931, which are arranged along the arrangement direction of the first axis to the second axis, i.e., along the arrangement direction of the N first drive gears 2391 and the N second drive gears 2392. The module and the theoretical number of teeth of the transmission gears 23931, the first drive gears 2391 and the second drive gears 2392 are all the same. One set of transmission gears 23931 includes N transmission gears 23931 arranged in the axial direction of the first drive gear 2391, one transmission gear 23931 close to the first drive gear 2391 includes a set of first engagement teeth 2393a, i.e., a set of first engagement teeth 2393a are arranged around the central axis of the transmission gear 23931, i.e., one end of the transmission component 2393 has N sets of first engagement teeth 2393a arranged in the direction of the first axis. One transmission gear 23931 close to the second drive gear 2392 includes a set of second engagement teeth 2393b, i.e., a set of second engagement teeth 2393b are arranged around the central axis of the transmission gear 23931, i.e., the other end of the transmission component 2393 has N sets of second engagement teeth 2393b arranged in the direction of the second axis.

[0139] In this configuration, each pair of adjacent gears in a first drive gear 2391, M transmission gears 23931, and a second drive gear 2392 meshes, where M ≥ 2 and is an even number. That is, the teeth of one first drive gear 2391 mesh with a set of first meshing teeth 2393a, and the teeth of one second drive gear 2392 mesh with a set of second meshing teeth 2393b. In the embodiments shown in Figures 15-17, the number of sets of transmission gears 23931 is 2. In other embodiments, the number of sets of transmission gears 23931 can also be 4, 6, 8, 10, etc. In other embodiments, the module and number of teeth of the transmission gears 23931, the first drive gear 2391, and the second drive gear 2392 can also be different.

[0140] In this way, with the first drive gear 2391 and the second drive gear 2392 being relatively small to facilitate the overall thinness of the folding device 100, the transmission component 2393 can make the distance between the first axis and the second axis as large as possible. This ensures that when the inward-folding folding device 100 is in the folded state, the radius of the teardrop-shaped screen space is as large as possible, so as to prevent excessive internal stress in the folding screen 10 and reduce the service life of the folding screen 10.

[0141] The aforementioned N first drive gears 2391 and N second drive gears 2392 can be integral structural components. Specifically, the N first drive gears 2391 and N second drive gears 2392 can be integrally molded components. In some examples, the N first drive gears 2391 and N second drive gears 2392 can be formed into an integral structural component using metal powder injection molding technology (MIM). In other examples, the N first drive gears 2391 and N second drive gears 2392 can be machined into an integral structural component using a computer numerical control (CNC) machine tool. Similarly, each set of transmission gears 23931 and the transmission shaft can be integral structural components. Thus, in the case where the diameters of the first drive gear 2391, the second drive gear 2392, and the transmission gear 23931 are too small, resulting in too few teeth, it can prevent the undercutting caused by the hobbing process in forming the first drive gear 2391, the second drive gear 2392, and the transmission gear 23931, which would otherwise result in low strength of the teeth of the first drive gear 2391, the second drive gear 2392, and the transmission gear 23931.

[0142] In this way, the coaxialities of the N first drive gears 2391 are better, and the phase angle tolerance between the first drive gears 2391 is easier to control; the coaxialities of the N second drive gears 2392 are better, and the phase angle tolerance between the second drive gears 2392 is easier to control; the coaxialities of the N transmission gears 23931 are better, and the phase angle tolerance between the transmission gears 23931 is easier to control, which can prevent tolerance accumulation, thereby ensuring the total coincidence of the N first drive gears 2391 and the N second drive gears 2392.

[0143] On this basis, the N first drive gears 2391 can form a gear shaft in an integral structure with the first rotating shaft 240, and the N second drive gears 2392 can form a gear shaft in an integral structure with the second rotating shaft 241. In this way, compared with the split structure of the first drive gears 2391 and the first rotating shaft 240 and the split structure of the second drive gears 2392 and the second rotating shaft 241, the assembly gap is reduced, the transmission mechanism 239 as a whole is more compact, occupies less space, and is more conducive to the thinning of the rotating shaft mechanism 23 and the folding device 100.

[0144] Please continue to refer to FIGS. 15-17, in the direction of the first axis (Y-axis direction): the teeth of two adjacent first drive gears 2391 have a first spacing, and the teeth of two adjacent second drive gears 2392 have a second spacing, that is, the teeth of two adjacent first drive gears 2391 are spaced apart, and the teeth of two adjacent second drive gears 2392 are spaced apart. Correspondingly, in a group of transmission gears 23931, the teeth of two adjacent transmission gears 23931 have a third spacing, that is, the teeth of two adjacent transmission gears 23931 are spaced apart. Specifically, in the direction of the first axis, the tooth width of a first drive gear 2391, the tooth width of a second drive gear 2392, and the tooth width of a transmission gear 23931 are the same, and the first spacing, the second spacing, and the third spacing are the same.

[0145] In this way, when the first drive gears 2391, the second drive gears 2392, and the transmission gears 23931 are machined, demolding is facilitated or the tool withdrawal space during CNC machining can be reserved. In addition, when the first rotating shaft 240, the second rotating shaft 241, and the transmission shaft are misaligned relative to the base 232 during unfolding and folding of the folding device 100, the projection of at least one of the N first drive gears 2391 on the N transmission gears 23931 in the arrangement direction of the first axis and the second axis is located on two transmission gears 23931, or the projection of at least one of the N first drive gears 2391 on the N second drive gears 2392 is located on two second drive gears 2392, thereby preventing the transmission mechanism 239 from being stuck, preventing the rotating shaft mechanism 23 from being stuck, and preventing the folding device 100 from being unfolded or folded.

[0146] In some other embodiments, the N first driving gears 2391 and the first rotating shaft 240 can also be in a split structure, and the N second driving gears 2392 and the second rotating shaft 241 can also be in a split structure. In some other embodiments, the N first driving gears 2391 can also be in a split structure, and the N second driving gears 2392 can also be in a split structure.

[0147] The coincidence degree ε1 of the first driving gear 2391 and the second driving gear 2392 can be greater than 1 or less than 1. It should be noted that in the embodiments shown in FIGS. 15-17, the coincidence degree of the first driving gear 2391 and the second driving gear 2392 is the same as the coincidence degree of the first driving gear 2391 and the transmission gear 23931, the coincidence degree of the two transmission gears 23931, and the coincidence degree of the transmission gear 23931 and the second driving gear 2392. The coincidence degree ε1 can be calculated by the aforementioned relationship formula one or the following relationship formula two: ε1=α1 / α z (relationship formula two)

[0148] Wherein, α1 is the angle of the first driving gear 2391 rotating from the meshing-in of a tooth of the first driving gear 2391 to the meshing-out of the tooth, which can be measured after the first driving gear 2391 and the second driving gear 2392 or the transmission gear 23931 meshing with the first driving gear 2391 are designed according to the thinning requirement of the folding device 100, α z is the pitch angle of the first driving gear 2391, specifically, the central angle corresponding to the pitch on an arbitrary circumference, α z The pitch angle can be calculated by the following relationship formula three: α z =360° / Z (relationship formula three)

[0149] Wherein, Z is the theoretical number of teeth of the first driving gear 2391, and it should be noted that the theoretical number of teeth Z is the number of teeth when the teeth of the first driving gear 2391 are evenly distributed along the circumference of 360°.

[0150] In some embodiments, please refer to FIG. 18, which is a schematic diagram of the meshing area of the first driving gear 2391. In FIG. 18, the initial reference position of the first driving gear 2391 rotating is when the first tooth of the two adjacent teeth of the first driving gear 2391 starts to mesh. The coincidence degree ε1 of the first driving gear 2391 and the second driving gear 2392 is less than 1, i.e. α1<α z, the former tooth is out of engagement, and the latter tooth has not yet entered engagement, i.e. the hatched area in the figure is the angle area of engagement of the first drive gear 2391 with the transmission gear 23931 or the second drive gear 2392. Thus, in the case that the transmission mechanism 239 only comprises one first drive gear 2391, when one of the first swing arm 233 and the second swing arm 234 rotates relative to the base 232, the rotational movement cannot be continuously transmitted to the other of the first swing arm 233 and the second swing arm 234, so that the first swing arm 233 and the second swing arm 234 cannot rotate at the same angle relative to the base 232, which makes the folding device 100 have poor jerk, poor synchronization and poor smoothness during unfolding and folding, and affects the user experience.

[0151] In this case, please refer to FIG. 19 and FIG. 20, FIG. 19 is a schematic diagram of the engagement area of a plurality of first drive gears 2391, and FIG. 20 is a schematic diagram of the engagement area of a plurality of first drive gears 2391. The foregoing phase angle β i satisfies the following relationship four and relationship five: β i ≤ α1 (relationship four)

[0152] That is, the sum of all phase angles of the N first drive gears 2391 is greater than or equal to α z - the difference between α1 and the phase angle of the adjacent two first drive gears 2391 is less than or equal to α1. In the embodiment shown in FIG. 19 and FIG. 20, the transmission of three first drive gears 2391 is taken as an example for schematic illustration, and the order of the sector diagrams in FIG. 19 and FIG. 20 from inside to outside is the arrangement order of the first drive gears 2391, i.e. the inside is the engagement area of the first first drive gear 2391, and the outside is the engagement area of the third first drive gear 2391. Two adjacent teeth of one first drive gear 2391, after the former tooth is out of engagement, the first drive gear 2391 rotates an angle of (α z - α1), and the latter tooth just starts to enter engagement. In the process of synchronous rotation of the N first drive gears 2391, after the i-th first drive gear rotates an angle of β i , the corresponding tooth of the i+1-th first drive gear starts to enter engagement.

[0153] If the phase angle β i satisfies the relationship four, one tooth of the i-th first drive gear 2391 has not yet been out of engagement or has just been out of engagement, and the corresponding tooth of the i+1-th first drive gear 2391 has already entered engagement. If β iIf the value is greater than α1, then one tooth of the i-th first drive gear 2391 has disengaged, and the corresponding tooth of the (i+1)-th first drive gear 2391 has not yet engaged, which will cause the transmission mechanism 239 to be interrupted.

[0154] If the phase angle β i If the aforementioned relation five is satisfied, then when the preceding tooth of the Nth first drive gear 2391 has just disengaged or has not yet disengaged, the following tooth of the first first drive gear 2391 has already engaged. If If the preceding tooth of the Nth first drive gear 2391 has disengaged and the following tooth of the first first drive gear 2391 has not yet engaged, the transmission mechanism 239 will also be interrupted.

[0155] Taking the preceding tooth of the first drive gear 2391 as a reference, the preceding tooth is staggered from the subsequent teeth by a phase angle β. i The preceding tooth of the N-1 first drive gears 2391 is considered as the preceding tooth of the first drive gear set composed of N first drive gears 2391, with a phase angle β. i Satisfying relations four and five, the first tooth of the first drive gear set has just disengaged or has not yet disengaged, while the second tooth of the first drive gear set has already begun to engage. Therefore, the total overlap ratio ε of the N first drive gears 2391 and the N second drive gears 2392 is ≥ 1.

[0156] Please refer to Figure 19, when When ε = 1, one tooth of the first drive gear set is in mesh; when When ε > 1; see Figure 20, when β i When α = 1, the total overlap ratio ε is at its maximum. At this time, from the moment one tooth of the first drive gear set enters engagement to the moment it disengages, the angle rotated by the first first drive gear 2391 is α = N × α1, and the total overlap ratio ε = N × ε1. In the embodiment shown in Figure 20, when N = 3, the first first drive gear rotates from 0° to α z Within the turning area, one tooth of the first drive gear set is in engagement; in α z ~2α z Within the turning area, two teeth of the first drive gear set are in a meshing state; in 2α z Within the angular region of ~3α1, three teeth of the first drive gear set are in a meshing state.

[0157] In this way, the transmission mechanism 239 can enable the first swing arm 233 and the second swing arm 234 to rotate at the same angle in opposite directions relative to the base 232, and the synchronization and smoothness are good, so that the synchronization and smoothness of the folding device are good, and the user experience is good.

[0158] In other embodiments, referring to FIG. 21, which is a schematic view of the meshing region of a plurality of first drive gears 2391, the overlapping region of the shadows in the meshing region of the same first drive gear 2391 is a plurality of tooth meshing corner regions. The coincidence degree ε1 of one first drive gear 2391 and one second drive gear 2392 is α1≥α z , and when the previous tooth is out of the meshing state or has not yet been out of the meshing state, the next tooth has already entered the meshing. In the embodiment shown in FIG. 21, 1<ε1<2 is taken as an example for illustration, that is, when the previous tooth of one first drive gear 2391 has not yet been out of the meshing, the next tooth has already entered the meshing, but the next tooth has not yet entered the meshing, at this time, α z <α1<2α z , and when β i =α1-α z , the total coincidence degree ε is maximum, at this time, the first drive gear group is in the maximum corner region of the (k+1) tooth continuous meshing state, and the total coincidence degree is ε=[α1+(N-1)×(α1-kα z )] / α z =ε1+(N-1)×ε(1-k.

[0159] By analogy, when the coincidence degree k of one first drive gear 2391 and one second drive gear 2392 is k<ε1<k+1, that is, when the first tooth of the adjacent teeth of one first drive gear 2391 is out of the meshing, the kth tooth has already entered the meshing, but the (k+1)th tooth has not yet entered the meshing, at this time, kα z <α1<(k+1)α z , and when β i =α1-kα z , the total coincidence degree ε is maximum, at this time, the first drive gear group is in the maximum corner region of the (k+1) tooth continuous meshing state, and the total coincidence degree is ε=[α1+(N-1)×(α1-kα z )] / α z =ε1+(N-1)×ε(1-k.

[0160] Therefore, the foregoing phase angle β i satisfies the following relationship six: β i ≤(α1-kα z ) (relationship six)

[0161] wherein k > 1 and k is an integer.

[0162] In other embodiments, please refer to FIG. 22 and FIG. 23, FIG. 22 is another partial structure diagram of the hinge mechanism 23 of the folding device 100 shown in FIG. 3, and FIG. 23 is an exploded structure diagram of the hinge mechanism 23 shown in FIG. 22. The difference between the embodiments shown in FIG. 22 and FIG. 23 and the embodiments shown in FIG. 7 and FIG. 8 is that the transmission component 2393 includes N first racks 23932 and N second racks 23933, the N first racks 23932 are arranged along the direction of the first axis, and the N second racks 23933 are arranged along the direction of the second axis, i.e. the N first racks 23932 are arranged along the axial direction of the first drive gear 2391, and the N second racks 23933 are arranged along the axial direction of the second drive gear 2392. The first racks 23932 extend along the first direction and can slide along the first direction relative to the base 232, the N second racks 23933 are arranged in parallel with and spaced apart from the N first racks 23932, and one second rack 23933 is fixedly connected with one first rack 23932. Wherein the first direction is the direction perpendicular to the plane in which the first axis and the second axis lie (Z-axis direction).

[0163] The N first racks 23932 can be an integral molded piece, or can be fixedly connected by welding, screw connection, clamping, etc. The N second racks 23933 can be an integral molded piece, or can be fixedly connected by welding, screw connection, clamping, etc. The N first racks 23932 and the N second racks 23933 can be an integral molded piece, or can be fixedly connected by welding, screw connection, clamping, etc. Based on this, the base 232 has a limiting protrusion 2322, and the integral structure formed by the N first racks 23932 and the N second racks 23933 has a limiting hole 23932a extending along the first direction (Z-axis direction), and the limiting protrusion 2322 is arranged in the limiting hole 23932a, so as to realize that the N first racks 23932 and the N second racks 23933 can slide along the first direction relative to the base 232. In other embodiments, the N first racks 23932 can also be a split structure, and the N second racks 23933 can also be a split structure.

[0164] On this basis, a first rack 23932 has a set of first meshing teeth 2393a, along the arrangement direction of the first rack 23932, the first meshing teeth 2393a of the i+1th first rack 23932 are staggered relative to the first meshing teeth 2393a of the ith first rack 23932 in the first direction by a certain distance, and the first meshing teeth 2393a of a first rack 23932 are engaged with the teeth of a first drive gear 2391. A second rack 23933 has a set of second meshing teeth 2393b, along the arrangement direction of the second rack 23933, the second meshing teeth 2393b of the i+1th second rack 23933 are staggered relative to the second meshing teeth 2393b of the ith second rack 23933 in the first direction by a certain distance, and the second meshing teeth 2393b of a second rack 23933 are engaged with the teeth of a second drive gear 2392.

[0165] In this way, the movement of one of the first swing arm 233 and the second swing arm 234 is transmitted to the other through the first rack 23932 and the second rack 23933, so that the distance between the first rotating shaft 240 and the second rotating shaft 241 can be more flexible, and the design and assembly difficulty of the transmission component 2393 is lower, which is conducive to the thinning of the folding device 100.

[0166] Please continue to refer to FIG. 22 and FIG. 23, the first light surface 2391a of the first drive gear 2391 is connected with the first swing arm 233, and the first drive gear 2391 and the first swing arm 233 are an integral structure; the second light surface 2392a of the second drive gear 2392 is connected with the second swing arm 234, and the second drive gear 2392 and the second swing arm 234 are an integral structure. In this way, the size of the first swing arm 233 and the first drive gear 2391 in the first axis direction can be saved, and the size of the second swing arm 234 and the second drive gear 2392 in the second axis direction can be saved, which is conducive to the overall structure of the rotating shaft mechanism 23 being more compact, and can reduce the difficulty of the first swing arm 233 and the first drive gear 2391 being integrally formed, and reduce the difficulty of the second swing arm 234 and the second drive gear 2392 being integrally formed. In other embodiments, the first swing arm 233 and the first drive gear 2391 can also be a split assembly structure. In other embodiments, the second swing arm 234 and the second drive gear 2392 can also be a split assembly structure.

[0167] On the basis of the above, please refer to FIG. 24 and FIG. 25, FIG. 24 is a schematic diagram of the opening and closing torsion curve of the folding device 100 shown in FIG. 3, and FIG. 25 is a schematic diagram of the relationship between the meshing area of the plurality of first driving gears 2391 and the rotation angle of the first swing arm 233 relative to the base 232, wherein the horizontal coordinate in FIG. 24 is the rotation angle of the first swing arm 233 or the second swing arm 234 relative to the base 232, and the vertical coordinate is the opening and closing torsion of the folding device 100. During the unfolding and folding process of the folding device 100, the load borne by the first swing arm 233, the first driving gear 2391, the second driving gear 2392 and the transmission component 239 generally presents a positive correlation with the opening and closing torsion of the folding device 100. Generally, the smaller the maximum load borne by a single gear tooth or meshing tooth, the smaller the stress and strain generated by the load borne by the gear tooth or meshing tooth, the more stable the transmission of the transmission mechanism 239, and the longer the service life. Therefore, the service life of the rotation shaft mechanism 23 and the folding device 100 is longer.

[0168] Based on this, in the case where the coincidence degree ε1 of the first driving gear 2391 and the second driving gear 2392 is less than 1, during the movement of the folding device 100 from the first state to the second state, when the first swing arm 233 rotates to the first rotation angle a relative to the base 232, the opening and closing torsion of the folding device 100 is the maximum torsion Tmax, and the phase angle β of the first driving gear 2391 relative to the second driving gear 2392 is i In the case where the relationship formula four and the relationship formula five are satisfied, the first rotation angle a and the phase angle β of the first driving gear 2391 relative to the second driving gear 2392 i Also satisfy the relationship formula seven:

[0169] That is, the sum of all phase angles of the N first driving gears 2391 is less than the sum of a and γ. One of the first state and the second state is the unfolded state, and the other is the folded state. γ is the rotation angle of the first first driving gear 2391 relative to the gear tooth currently in the meshing state when the first first driving gear 2391 just enters the meshing state when the folding device 100 is in the first state, and γ≥0°. When γ=0°, the gear tooth currently in the meshing state of the first first driving gear 2391 just enters the meshing state when the folding device 100 is in the first state. In other embodiments, when γ>0, the gear tooth currently in the meshing state of the first first driving gear 2391 has been rotated by an angle γ since it just entered the meshing state when the folding device 100 is in the first state. It should be noted that γ can be set by the structural design of the first driving gear 2391 and the first swing arm 233 and the assembly with the base 232, and the first rotation angle a and Tmax can be obtained by testing the opening and closing torsion of the folding device 100. In this way, it is beneficial to have more first driving gears in the meshing state in the first driving gear set at the position where the opening and closing torsion of the folding device 100 is the largest, so that the load borne by a single gear tooth is smaller, which is beneficial to prolong the service life of the rotation shaft structure and the folding device 100.

[0170] In the curve diagram shown in FIG. 24, curve L1 is a relationship curve between the opening and closing torsion of the folding device 100 and the rotation angle of the first swing arm 233 relative to the base 232 in the process that the folding device 100 moves from the unfolded state to the folded state, i.e., the first state is the unfolded state and the second state is the folded state. When the folding device 100 is in the unfolded state, the rotation angle of the first swing arm 233 relative to the base 232 is 0°. When the folding device 100 is in the folded state, the rotation angle of the first swing arm 233 relative to the base 232 is 90°. The first rotation angle a is the rotation angle a1. The maximum torsion value Tmax is T1max. Curve L2 is a relationship curve between the opening and closing torsion of the folding device 100 and the rotation angle of the first swing arm 233 relative to the base 232 in the process that the folding device 100 moves from the folded state to the unfolded state, i.e., the first state is the folded state and the second state is the unfolded state. When the folding device 100 is in the folded state, the rotation angle of the first swing arm 233 relative to the base 232 is 0°. When the folding device 100 is in the unfolded state, the rotation angle of the first swing arm 233 relative to the base 232 is 90°. The first rotation angle a is the rotation angle a2. The maximum torsion value Tmax is T2max. The direction of T2max is opposite to that of T1max. The rotation angle a2 can be the same as or different from the rotation angle a1. The absolute value of T1max can be the same as or different from that of T2max. The present application does not limit this.

[0171] On this basis, when the first swing arm 233 rotates by a second rotation angle b relative to the base 232, the opening and closing torsion of the folding device 100 is T1, and 0.4≤T1 / Tmax≤0.6. When the first swing arm 233 rotates from the second rotation angle b to the first rotation angle a relative to the base 232, the opening and closing torsion of the folding device 100 gradually increases. The second rotation angle b is smaller than the phase angle β. i The relationship eight is satisfied:

[0172] i.e., the sum of all phase angles of the N first driving gears 2391 is smaller than the sum of b and γ. In this way, the opening and closing torsion of the folding device 100 is still large at the position near the peak value of the opening and closing torsion of the folding device 100. Before the opening and closing torsion of the folding device 100 reaches the maximum value, the number of the first driving gears 2391 in the meshing state of the first driving gear set is large, so that the load on a single tooth is small, which is beneficial to prolong the service life of the rotating shaft mechanism 23 and the folding device 100. In the curve diagram shown in FIG. 24, the second rotation angle b is the rotation angle b1 when the first state is the unfolded state and the second state is the folded state. The second rotation angle b is the rotation angle b2 when the first state is the folded state and the second state is the unfolded state. The rotation angle b2 can be the same as or different from the rotation angle b1. The present application does not limit this.

[0173] On the basis of the above, please refer to FIG. 24 and FIG. 25, the first rotation angle a also satisfies the relationship nine: a < α1-γ (relationship nine)

[0174] In this way, at the position where the opening and closing torsion of the folding device 100 is the largest, all the first driving gears 2391 are in meshing state, which is conducive to prolonging the service life of the rotating shaft mechanism 23, and is also conducive to the position of the protruding part of each damping cam in the damping structure, ensuring the stability of the folding device in the unfolded state or the folded state.

[0175] On the basis of the above, when the first swing arm rotates a third rotation angle c relative to the base, the opening and closing torsion of the folding device is T2, and 0.4≤T2 / Tmax≤0.6, specifically, T2=T1; when the first swing arm rotates from the first rotation angle a to the third rotation angle c relative to the base, the opening and closing torsion of the folding device gradually decreases, and the third rotation angle c also satisfies the relationship ten: c≤α1-γ (relationship ten)

[0176] In this way, at the position near the peak of the opening and closing torsion of the folding device 100, the opening and closing torsion of the folding device 100 is still large, and within a certain rotation angle range after the opening and closing torsion of the folding device 100 reaches the maximum value, all the first driving gears 2391 are in meshing state, so the load on a single gear tooth is small, which is conducive to prolonging the service life of the rotating shaft mechanism 23 and the folding device 100. In the curve diagram shown in FIG. 24, the third rotation angle c is c1 when the first state is the unfolded state and the second state is the folded state; the third rotation angle c is c2 when the first state is the folded state and the second state is the unfolded state. c2 can be the same as c1 or different from c1, which is not limited in the present application.

[0177] The above takes the folding device of the in-folding type as an example to describe the structure of the rotating shaft mechanism 23 of the folding device 100.

[0178] Please refer to FIG. 26-FIG. 28, FIG. 26 is a structural schematic diagram of the rotating shaft mechanism 23 of the folding device 100 shown in FIG. 4 in the unfolded state, FIG. 27 is an exploded structural diagram of the rotating shaft mechanism 23 shown in FIG. 26, and FIG. 28 is a partial structural schematic diagram of the rotating shaft mechanism 23 shown in FIG. 27. The difference between the embodiments shown in FIG. 26-FIG. 28 and the embodiments shown in FIG. 15 and FIG. 16 is that the rotating shaft structure does not include the connecting piece 237, and the door plate 238 further includes a third door plate 2383 and a fourth door plate 2384.

[0179] The first swing arm 233 and the second swing arm 234 are located on both sides of the base 232. One end of the first swing arm 233 is rotationally connected to the base 232 through a first rotating shaft 240, and the other end is slidingly connected to the first door plate 2381. The third door plate 2383 is located between the base 232 and the first door plate 2381, and the third door plate 2383 is rotationally connected to the first door plate 2381 and rotationally connected to the base 232. Similarly, one end of the second swing arm 234 is rotationally connected to the base 232 through a second rotating shaft 241, and the other end is slidingly connected to the second door plate 2382. The fourth door plate 2384 is located between the base 232 and the second door plate 2382, and the fourth door plate 2384 is rotationally connected to the base 232 and rotationally connected to the second door plate 2382. The first door plate 2381 is used to be connected with the first shell 21, and the second door plate 2382 is used to be connected with the second shell 22.

[0180] Please refer to FIG. 26 and FIG. 29, FIG. 29 is a structural schematic diagram of the rotating shaft mechanism 23 in the folding state shown in FIG. 26. When the first shell 21 rotates under the action of external force, the first door plate 2381 and the first swing arm 233 rotate with the first shell 21, thereby driving the third door plate 2383 to rotate. When the second shell 22 rotates under the action of external force, the second door plate 2382 and the second swing arm 234 rotate with the second shell 22, thereby driving the fourth door plate 2384 to rotate, so as to realize the relative rotation between the first shell 21 and the second shell 22, and move the folding device 100 between the unfolded state and the folded state.

[0181] The third swing arm 235 and the fourth swing arm 236 are located on both sides of the base 232. One end of the third swing arm 235 is rotationally connected to the base 232 through a fifth rotating shaft 245, and the other end is slidingly connected to the first door plate 2381. Similarly, one end of the fourth swing arm 236 is rotationally connected to the base 232 through a sixth rotating shaft 246, and the other end is slidingly connected to the second door plate 2382. The connection form of the third swing arm 235 to the base 232 through the fifth rotating shaft 245 and the connection form of the fourth swing arm 236 to the base 232 through the sixth rotating shaft 246 can refer to the connection form between the first rotating shaft 240 and the base 232 of the first swing arm 233, which will not be described here.

[0182] Please refer to Figures 28 and 30 together. Figure 30 is a cross-sectional view of the rotating shaft mechanism 23 shown in Figure 28. Specifically, (a) in Figure 30 is a cross-sectional view of the rotating shaft mechanism 23 at line CC, (b) is a cross-sectional view of the rotating shaft mechanism 23 at line DD, and (c) is a cross-sectional view of the rotating shaft mechanism 23 at line EE. The transmission mechanism 239 does not include the transmission component 2393. Of the N first drive gears 2391 and N second drive gears 2392, one first drive gear 2391 and one second drive gear 2392 directly mesh. This allows the distance between the first rotating shaft 240 and the second rotating shaft 241 to be as close as possible, which helps reduce the thickness of the rotating shaft mechanism 23 in the folded state, and thus facilitates the thinning of the outward-folding folding device 100. In the embodiments shown in Figures 28 and 30, there are three first drive gears 2391 and three second drive gears 2392. The theoretical number of teeth z for the first drive gears 2391 and the second drive gears 2392 is eight. The phase angle β between any two adjacent first drive gears 2391 is... i Both are 11.25°.

[0183] The first smooth surface 2391a of the first drive gear 2391 is connected to the first swing arm 233, and the first drive gear 2391 and the first swing arm 233 are an integral structural component; the second smooth surface 2392a of the second drive gear 2392 is connected to the second swing arm 234, and the second drive gear 2392 and the second swing arm 234 are an integral structural component.

[0184] In other embodiments, please refer to Figures 31-33. Figure 31 is a partial structural schematic diagram of the rotating shaft mechanism 23 shown in Figure 26; Figure 32 is a structural schematic diagram of the rotating shaft mechanism 23 shown in Figure 31 in a folded state; and Figure 33 is a partial structural schematic diagram of the rotating shaft mechanism 23 shown in Figure 31. The embodiments shown in Figures 31-33 differ from those shown in Figures 28 and 30 in that the number of first drive gears 2391 and second drive gears 2392 are both two, and the phase angle β between any two adjacent first drive gears 2391 is... i All angles are 22.5°. In the embodiments shown in Figures 28 and 31, the first swing arm 233, the first rotating shaft 240, and the first drive gear 2391 are integrally formed, as are the second swing arm 234, the second rotating shaft 241, and the second drive gear 2392. Along a direction perpendicular to the first axis, the first drive gear 2391 is fixed to one end of the first swing arm 233 near the base 232, and the second drive gear 2392 is fixed to one end of the second swing arm 234 near the base 232. Specific technical effects can be found above and will not be repeated here.

[0185] Please refer to Fig. 27 and Fig. 34, Fig. 34 is a schematic diagram of the partial structure of the rotating shaft mechanism 23 shown in Fig. 31, the damping structure 244 is arranged on the third swing arm 235 and the fourth swing arm 236, the structure of the damping structure 244 and the connecting structure of the fifth rotating shaft 245, the sixth rotating shaft 246, the third swing arm 235 and the fourth swing arm 236 can refer to the connecting structure of the damping structure 244 and the first rotating shaft 240, the second rotating shaft 241, the first swing arm 233 and the second swing arm 234 in the foregoing embodiment shown in Fig. 16, which will not be repeated here. That is, when the first swing arm 233 rotates relative to the base 232, the first damping cam 2441 can be driven to rotate by the first door plate 2381 and the third swing arm 235. When the second swing arm 234 rotates relative to the base 232, the third damping cam 2443 can be driven to rotate relative to the base 232 by the second door plate 2382 and the fourth swing arm 236.

[0186] In the description of the present specification, specific features, structures, materials or characteristics can be combined in any one or more embodiments or examples in a suitable manner.

[0187] Finally, it should be noted that: the above examples are only used to illustrate the technical solutions of the present application, and not to limit them; although the present application has been described in detail with reference to the foregoing examples, those skilled in the art should understand: it can still modify the technical solutions recorded in the foregoing embodiments, or make equivalent replacement for part of the technical features; and these modifications or replacements do not make the essence of the corresponding technical solutions deviate from the spirit and scope of the technical solutions of the embodiments of the present application.

Claims

1. A rotation shaft mechanism characterized by comprising: Comprise: a base; a first swing arm rotatably connected with the base; a second swing arm rotatably connected with the base; N first driving gears, the N first driving gears are fixedly connected with the first swing arm, the N first driving gears are coaxially arranged; along the arrangement direction of the N first driving gears, the gear teeth of the i+1 first driving gear are staggered relative to the gear teeth of the i first driving gear by a phase angle β i ; N second drive gears fixedly connected with the second swing arm, the N second drive gears coaxially arranged; one of the second drive gears meshes with one of the first drive gears; the second drive gears and the first drive gears are used to drive the first swing arm and the second swing arm to synchronously and reversely rotate relative to the base, so as to drive the rotating shaft mechanism to move between the unfolded state and the folded state; wherein β i > 0°, 1≤i≤N-1, N≥2, and N, i are integers.

2. The rotating shaft mechanism according to claim 1, wherein the coincidence degree of one of the first drive gears and one of the second drive gears is ε1 < 1; The phase angle β i satisfies: wherein α z is the first drive gear, α1 is the angle of rotation of the first drive gear from the engagement of one tooth of the first drive gear to the disengagement of the one tooth of the first drive gear.

3. The rotating shaft mechanism according to claim 1, wherein the coincidence degree of one of the first drive gears and one of the second drive gears is k < ε1 < k + 1; The phase angle β i satisfies: β i ≤α1-kα z ； wherein k≥1 and k is an integer; a z is the first drive gear tooth pitch angle, a1 is the angle of rotation of the first drive gear from the engagement of one tooth of the first drive gear to the disengagement of the one tooth of the first drive gear.

4. The rotating shaft mechanism according to any one of claims 1-3, wherein along the axial direction of the first drive gears: the teeth of adjacent two of the first drive gears are arranged at intervals, and the teeth of adjacent two of the second drive gears are arranged at intervals.

5. The rotating shaft mechanism according to any one of claims 1-4, wherein the N first drive gears are an integral structural member; and / or the N second drive gears are an integral structural member.

6. The rotating shaft mechanism according to claim 5, wherein the peripheral surface of the first drive gear comprises a first smooth surface and a first tooth surface, the first smooth surface is located on the side of the first tooth surface away from the second drive gear, and is in contact with the surface of the first swing arm, the first drive gear and the first swing arm are an integral structural member; and / or the peripheral surface of the second drive gear comprises a second smooth surface and a second tooth surface, the second smooth surface is located on the side of the first tooth surface away from the first drive gear, and is in contact with the surface of the second swing arm, the second drive gear and the second swing arm are an integral structural member.

7. The rotating shaft mechanism according to any one of claims 1-6, wherein the rotating shaft mechanism further comprises a transmission component, the transmission component is located between the first drive gears and the second drive gears, the transmission component meshes with the N first drive gears and meshes with the N second drive gears.

8. The rotation shaft mechanism according to claim 7, wherein the transmission component comprises: M groups of transmission gears, the M groups of transmission gears are arranged along the arrangement direction of the N first drive gears and the N second drive gears; one group of the transmission gears comprises N transmission gears arranged along the axial direction of the first drive gears, every adjacent two of the first drive gears, the M transmission gears and the second drive gears mesh with each other, M ≥ 2 and is an even number.

9. The rotation shaft mechanism according to claim 7, wherein the transmission component comprises: N first racks arranged along the axial direction of the first drive gears, the first racks extend in a first direction and can slide in the first direction relative to the base, one of the first racks meshes with one of the first drive gears; N second gear racks arranged along the axial direction of the first driving gear, the N second gear racks being parallel to and spaced apart from the N first gear racks, one second gear rack being fixedly connected to one first gear rack; and one second gear rack being engaged with one second driving gear; The first direction is perpendicular to the plane in which the central axis of the first driving gear and the central axis of the second driving gear are located.

10. The revolute mechanism according to any one of claims 1-9, wherein, The rotating shaft mechanism further comprises: A first damping cam arranged on the base, the first damping cam being capable of rotating relative to the base when the first swing arm rotates relative to the base; A second damping cam arranged on the base and capable of sliding relative to the base along the axial direction of the first driving gear, the second damping cam being in contact with the first damping cam; A first elastic member arranged on the base and configured to apply an elastic force to the second damping cam, the elastic force being directed towards the first damping cam.

11. The rotation shaft mechanism according to claim 10, wherein The rotating shaft mechanism further comprises: A third damping cam arranged on the base, the third damping cam being capable of rotating relative to the base when the second swing arm rotates relative to the base; A fourth damping cam arranged on the base and capable of sliding relative to the base along the axial direction of the second driving gear, the fourth damping cam being in contact with the third damping cam; A second elastic member arranged on the base and configured to apply an elastic force to the fourth damping cam, the elastic force being directed towards the third damping cam.

12. The rotating shaft mechanism according to claim 11, wherein The second damping cam and the fourth damping cam are an integral structure.

13. A support device characterized by comprising: It comprises: A first housing; A second housing; A rotating shaft mechanism according to any one of claims 1-12, the rotating shaft mechanism being located between the first housing and the second housing, the first swing arm being connected to the first housing, and the second swing arm being connected to the second housing.

14. A folding apparatus, characterized by It comprises: A support device according to claim 13; A folding screen comprising a first portion, a second portion and a third portion connected in sequence, the first portion being fixed to the first housing, the third portion being fixed to the second housing, and the second portion being supported by the rotating shaft mechanism.

15. The folding device according to claim 14, wherein The degree of coincidence of one first driving gear and one second driving gear is ε1<1; In the process that the folding device moves from the first state to the second state, when the first swing arm rotates a first rotation angle a relative to the base, the opening and closing torsion of the folding device is a maximum torsion value Tmax; the first rotation angle a and the phase angle β satisfy: i satisfies: In the first state and the second state, one of them is the unfolded state, and the other is the folded state; γ is the angle of rotation of the first driving gear when it is about to enter the engaged state relative to the tooth currently in the engaged state when the folding device is in the first state, and γ≥0.

16. The folding device according to claim 15, wherein When the first swing arm rotates a second rotation angle b relative to the base, the opening and closing torsion of the folding device is T1, and 0.4≤T1 / Tmax≤0.6, when the first swing arm rotates from the second rotation angle b to the first rotation angle a relative to the base, the opening and closing torsion of the folding device gradually increases, the second rotation angle b and the phase angle β i satisfies:

17. The folding device according to claim 15 or 16, wherein The first rotation angle a also satisfies: a < a1- g.

18. The folding device according to claim 17, characterized in that, when the first swing arm rotates a third rotation angle c relative to the base, the opening and closing torsion of the folding device is T2, and 0.4 < T2 / Tmax < 0.6, when the first swing arm rotates from the first rotation angle a to the third rotation angle c relative to the base, the opening and closing torsion of the folding device gradually decreases, and the third rotation angle c also satisfies: c < a1- g.

Images